US8301331B2 - Method and device for the calibration or diagnosis of a motor vehicle brake system having a cyclically operated pump - Google Patents

Method and device for the calibration or diagnosis of a motor vehicle brake system having a cyclically operated pump Download PDF

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US8301331B2
US8301331B2 US12/739,456 US73945608A US8301331B2 US 8301331 B2 US8301331 B2 US 8301331B2 US 73945608 A US73945608 A US 73945608A US 8301331 B2 US8301331 B2 US 8301331B2
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Prior art keywords
pump
operating
voltage
motor vehicle
interpulse period
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US20110184606A1 (en
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Faouzi Attallah
Tobias Scheller
Tom Robert
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Aumovio Germany GmbH
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Continental Teves AG and Co OHG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/404—Control of the pump unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/404—Control of the pump unit
    • B60T8/4059—Control of the pump unit involving the rate of delivery

Definitions

  • the invention relates to a method and to a device for the calibration or diagnosis of a motor vehicle brake system having a pump operated in a pulsed fashion.
  • Such a motor vehicle brake system is usually provided with two two-way valves that prevent locking of the wheels of a motor vehicle by their alternate switching.
  • the two-way valves are usually driven by means of a control unit designed as a so-called microcontroller. Details on the functioning of a motor vehicle brake system may be gathered, for example, from the specialist book by Dubbel, Taschenbuch für den Maschinenbau [Manual of engineering], Springer Verlag, Heidelberg, 20th Ed. 2001, ISBN 3-540-67777-1, section Q/vehicle engineering, which is incorporated by reference. It is normal to provide a pump for pumping brake fluid in such a motor vehicle brake system.
  • Optimized driving of the two two-way valves can be achieved by driving the two two-way valves as a function of the brake line pressure between a master brake cylinder and a wheel brake cylinder of a wheel brake.
  • This brake line pressure is denoted below as admission pressure.
  • DE 10 2005 041 556 A1 which is incorporated by reference, discloses a method for determining an admission pressure prevailing between a master brake cylinder and an inlet valve of a wheel brake cylinder of a motor vehicle brake system.
  • the admission pressure is determined by taking account of the profile of a run-on voltage of a motor, operated in a pulsed fashion, of the pump.
  • a plurality of characteristic variables of the voltage profile are measured and used in each case to determine an admission pressure value, there taking place an evaluation of the quality and/or reliability of the measured characteristic variables, a filtering and/or conditioning of the characteristic variables and/or of the admission pressure values determined therefrom in the event of lack of quality and/or reliability of the measured characteristic variables, averaging of the admission pressure values coming from the different characteristic variables, account being taken only of pressure values of similar magnitude, and the admission pressure values being averaged over time in order to damp fluctuations.
  • a correspondingly determined characteristic curve is stored in a data memory of a control unit controlling the motor vehicle brake system.
  • the two two-way valves are driven according to the admission pressure calculated with the aid of the characteristic curve.
  • the first step to this end is to determine for a reference pump at least one parameter that represents the electromotive force of the reference pump motor, this being done repeatedly (that is to say multiply in sequence) under defined stipulations.
  • a statistical characteristic variable is derived from the values of the parameter that are determined for the reference pump.
  • reference pump use is made here, in particular, of a pump used to carry out reference measurements in the development phase of the brake system in the context of a prototype of the vehicle brake system.
  • the parameter considered is determined, in particular, from the motor voltage falling at the reference pump.
  • the defined stipulations are a set of test conditions that relate, for example, to the installation of the pump in a special type of a motor vehicle brake system, the temperature or the chemical composition of the brake fluid.
  • a further stipulation is that the parameter be determined in a load free state of the brake system, that is to say without actuation of the brake pedal.
  • the same parameter is determined under stipulations for an operating pump that correspond—in particular, under the same stipulations as far as possible.
  • operating pump is the pump that is to be calibrated, which is a component of a motor vehicle brake system intended to be installed in a motor vehicle or already installed in the motor vehicle.
  • the operating pump and the associated brake system are in this case in particular of the same type as the reference pump and, especially, the brake system associated therewith.
  • a corresponding statistical characteristic variable is also derived from the values that are determined for the reference pump.
  • the ratio is generally a function of the characteristic variables that are determined for reference pump and operating pump.
  • VZ g ( K RP ,K BP )
  • the ratio is calculated as quotient of the characteristic variables.
  • the ratio is used to calibrate the operating pump by adapting a characteristic curve of the operating pump to a correspondingly prescribed characteristic curve of the reference pump as a function of this ratio.
  • the characteristic curve of the operating pump stems from the characteristic curve of the reference pump in that this characteristic curve of the reference pump is calculated with the ratio or by means of a function dependent on the ratio.
  • the characteristic curve of the operating pump is consequently a function of the characteristic curve of the reference pump and of the ratio.
  • the characteristic curve can be used in a form adapted to the conditions of the operating pump.
  • the characteristic curve for the reference pump can in this case include any desired functional relationship between the parameter and a variable describing the behavior of the brake system. In this way, findings obtained for the reference pump during the development phase of the motor vehicle brake system can also be used to the full extent for the operating pump.
  • the characteristic curve of the reference pump is available at any time for calculation with the at least one ratio. In this case, it is stored in particular in a data memory of the control unit designed as microcontroller. Consequently, the calibration of the operating pump can be carried out anew at any time.
  • it is, in particular, provided to carry out a first calibration before the motor vehicle is delivered. It is possible thereby to eliminate manufacturing tolerances in the production of the operating pump and the entire motor vehicle brake system, without the need to determine the characteristic curve for each operating pump individually from the beginning. It is preferred to carry out further calibrations at periodical intervals, for example in the course of maintenance of the motor vehicle in a workshop. Aging and wear processes of the operating pump and of the entire motor vehicle brake system can also be eliminated in this way.
  • the characteristic curves represent a functional relationship between the at least one parameter and a brake line pressure of the motor vehicle brake.
  • the brake line pressure can be determined in this way without the use of a pressure transducer adapted to the operating state of the operating pump.
  • the adaptation of the characteristic curve measured for the reference pump to the operating pump yields an increase in the accuracy during the determination of the brake line pressure.
  • the brake line pressure calculated by means of the characteristic curve is, in particular, the pressure of the brake line connected on the discharge side to the pump, that is to say the so-called admission pressure. Given the exact, knowledge of this admission pressure, it is possible for the switching instant of the two two-way valves to be prescribed exactly by means of the control unit. A particularly controlled braking operation can be achieved in this way. Pressure surges such as can arise in the event of unfavorable switching instants of the two two-way valves, and which impair the controllability of the motor vehicle during the braking operation, are therefore reliably avoided.
  • the characteristic curve can also supply a throughflow rate and/or an operating temperature of the respective pump as a function of the at least one parameter.
  • the ratio is used to effect a diagnosis of the operating pump by checking whether the ratio lies inside or outside a prescribed tolerance range. If the ratio or the characteristic variable lies outside the tolerance range, this means that the operating pump deviates strongly from the reference pump in terms of its operating behavior. The operating pump is identified as defective in this case.
  • the above-described checking takes place in the course of a normal calibration operation, for example.
  • the checking can also be undertaken to this end independently of the pump calibration.
  • the statistical evaluation of the parameters determined for the reference pump and/or for the operating pump is preferably performed by plotting the acquired parameter values in respective histograms for the reference pump and for the operating pump, the statistical characteristic variables used for the calculation of the ratio being determined from the respective histogram.
  • a histogram is understood below as a frequency distribution of measured values of the parameter that occur over a prescribed number of operating clocks.
  • the voltage present across the motor terminals after termination of a drive pulse of the pump voltage is preferably used as parameter representative of the electromotive force of the pump motor. This voltage is represented in particular by the first acquired voltage value (denoted as U Off below) inside an interpulse period following the pulse.
  • the voltage present on average over time during the interpulse period is used as parameter in a further expedient design of the method.
  • This voltage is, in particular, represented in metrological terms by the average value (denoted below as U AVER ) of a plurality of voltage values acquired during the interpulse period. It has emerged that these two parameters are to a high degree specific to each individual pump, and enable a particularly precise conclusion regarding the operating behavior of this pump.
  • the following parameters of the pump voltage are ascertained optionally—in addition or as an alternative to the above variables—and taken into account when determining the statistical characteristic variables, in particular when creating the histograms, if appropriate:
  • Each of these values can easily be acquired by carrying out a measurement of the motor voltage of the pump motor and by correlating this measurement with the known operating clock of the pump. If appropriate, a simple algebraic operation such as summation or averaging, or the calculation of a compensating straight line, is further carried out. It is thereby possible for a voltage measuring arrangement to be integrated in a simple way in circuit logic of a control unit designed as microcontroller.
  • the clocking of the respective pump is preferably firmly prescribed within the scope of the stipulations. Consequently, the ratio of the duration of a pulse to the duration of a following interpulse period is always the same for the reference pump and for the operating pump.
  • the measured values for the reference pump and for the operating pump therefore come under the same stipulations for the driving of the pump motor. It may also expressly be pointed out that the intention here is also to include stipulations in the case of which the clocking is changed several times one after another in a defined way during a measurement. It is possible with the aid of such a stipulation for the characteristic curve of the operating pump to be acquired in a further context as if only a single clocking were to be used for measurement.
  • the at least one parameter is normalized to a further one of the above named parameters.
  • the characteristic variable that is to say, in particular, the mean value
  • the first step is for a mathematical distribution function to be adapted to each histogram by means of a numerical regression method (Fit).
  • the statistical characteristic variables are obtained in this case from the adapted distribution function.
  • a Gaussian distribution function in particular, is used as distribution function.
  • the ratios of a plurality of parameters are calculated with respect to one another in order to form a total ratio.
  • a measured variable that depends on all the parameters on which the ratios are based, it is thereby possible to determine a more accurate calibration and thus a characteristic curve for the operating pump that is better adapted to reality.
  • VZ ⁇ ⁇ tilde over (g) ⁇ ( VZ 1 , . . . , VZ N ),
  • This total ratio is advantageously a weighted sum of the ratios. In the simplest case, this is the arithmetic mean value of all the ratios. However, it is also possible to take account of the influence of individual parameters on the characteristic curve by means of weighting factors. In general, the total ratio is therefore yielded as a linear combination of the individual ratios, the formal expression being
  • a device for the calibration of a motor vehicle brake system having a pump operated in a pulsed fashion having a control unit designed to carry out the above-described method.
  • This control unit is designed, in particular, as a microcontroller, and is therefore small and compact.
  • the individual refinements of the method are to be transferred to the device mutatis mutandis together with its advantages.
  • FIG. 1 shows a schematic of a motor vehicle brake system
  • FIG. 2 shows a detail of a motor voltage measured at a motor of a pump, in a time/voltage diagram
  • FIG. 3 shows a method block diagram for the calibration of the pump
  • FIG. 4 shows a histogram of the initial voltage of a reference pump
  • FIG. 5 shows a further histogram of the initial voltage of an operating pump
  • FIG. 6 shows for the reference pump and for the operating pump a respective characteristic curve that describes the admission pressure of the respective pump as a function of the respective initial voltage.
  • FIG. 1 shows a slip-controlled motor vehicle brake system 1 of a motor vehicle.
  • Each wheel of the motor vehicle is assigned a wheel brake circuit.
  • Two wheel brake circuits each are combined to form a brake circuit. Since the design of the overall total of four wheel brake circuits is equivalent, only one wheel brake circuit is shown in FIG. 1 for the purpose of greater clarity.
  • the motor vehicle brake system 1 has a master brake cylinder 2 that can be actuated by means of a brake pedal 3 and applies to both brake circuits simultaneously the braking force of the brake pedal 3 boosted by a brake booster.
  • the master brake cylinder 2 is connected to a wheel brake cylinder 8 ′ of a wheel brake 8 of a wheel by means of a brake line 4 and a control device 5 that comprises a hydraulic device 6 and a control unit 7 .
  • the hydraulic unit 6 comprises two two-way valves 9 , 10 , a return line 12 , a low-pressure accumulator 13 , a second return line 12 ′ and a pump 14 driven by a motor 15 .
  • the pump 14 is designed as a radial piston pump and has an intake valve 16 on the intake side and a discharge valve 17 on the discharge side.
  • the control unit 7 which is designed as a microcontroller, drives the two two-way valves 9 , 10 and the pump 14 .
  • the control unit 7 is assigned a tachometer 18 , by means of which the instantaneous rotational speed of the wheel can be acquired.
  • the first two-way valve 9 is open in the currentless state and the second two-way valve 10 is closed in the currentless state.
  • the brake fluid is displaced in the direction R 1 toward the wheel brake cylinder 8 ′.
  • the braking force is thereby transmitted directly onto the wheel brake cylinder 8 ′.
  • the wheel of the motor vehicle is braked.
  • the rotational speed of all four wheels and of the motor vehicle is constantly comprised by means of the control unit 7 . If the rotational speed of a wheel reduces rapidly by comparison with the other wheels, slip is present. The wheel threatens to lock.
  • control unit 7 is used to switch over the two two-way valves 9 , 10 simultaneously or virtually simultaneously and in a mutually coordinated fashion.
  • the two-way valve 9 is now closed such that the braking force 9 can no longer act on the wheel brake cylinder.
  • brake fluid is discharged in the direction R 2 toward the low-pressure accumulator 13 via the now open two-way valve 10 .
  • the wheel brake cylinder 8 is relieved of load in this way.
  • the wheel is freed from the wheel brake again such that its rotational speed again equals the speed of the motor vehicle.
  • the pump 14 the brake fluid is conveyed back in the direction of the brake line 4 from its intake side with its intake valve 16 in the direction R 3 of its discharge side with its discharge valve 17 .
  • the two two-way valves 9 , 10 are switched over again in a mutually coordinated fashion such that, in turn, the initial situation with an open two-way valve 9 and a closed two-way valve 10 is present.
  • the braking force exerted on the brake pedal 3 now acts again on the wheel brake cylinder 10 .
  • the vehicle is further braked until, in turn, there occurs a significant braking of the wheel associated with a slip, and the two two-way valves 9 , 10 are switched over anew.
  • the electric motor 15 of the pump 14 is based in principle on a separately excited DC machine for driving the pump impeller, whose speed is controlled via a pulse width modulation (PWM) of a constant supply voltage.
  • the speed of the pump impeller can be set in a plurality of ranges in this case.
  • the discharge rate of the pump 14 is prescribed, in turn, via the speed of the pump impeller.
  • the duration of the pulse, and thus the residual clock duration of the interpulse period, following the pulse, of the supply voltage present at the motor are modulated within a fixed time interval (a PWM cycle or operating clock, for example with a period of 60 ms).
  • a maximum drive level of the motor corresponds to a supply voltage present over the entire time interval of the operating clock.
  • the supply voltage of the motor 15 is switched off after a certain time (for example after 40 ms), remains switched off for the residual duration of the operating clock (20 ms in the example) and is switched on again at the start of the next operating clock.
  • the duration of the interpulse period increases by comparison with the duration of the pulse for a prescribed duration of the operating clock.
  • the control unit can be used to control the speed of the pump impeller, and thus the discharge rate of the pump 14 in a wide range coordinated with the respective required discharge.
  • FIG. 2 shows the motor voltage U M dropping at the motor 15 in a time/voltage diagram.
  • the operating clock of the supply voltage (not illustrated in FIG. 2 ) is essentially simulated in the motor voltage U M : a pulse 19 of pulse width E is followed by an interpulse period 20 of the residual clock duration A.
  • the pulse 19 and the interpulse period 20 together constitute an operating clock.
  • the interpulse period 20 is followed by a pulse 19 ′ of a following operating clock.
  • the motor voltage U M corresponds essentially to the supply voltage.
  • the motor voltage U M does not drop to zero during the interpulse period 20 . The reason for this is that the motor 15 runs on directly after being switched off and induces a voltage.
  • the motor 15 consequently acts somewhat like a generator.
  • the motor voltage U M continues to drop.
  • P Also plotted in FIG. 2 are a plurality of parameters P that all relate to the profile of the motor voltage U M during the interpulse period. In detail, these are:
  • the characteristic curve p v (U RP Off ) is stored in a data memory of the control unit 7 . Consequently, during the later operation of the motor vehicle brake system 1 of an end user in which an operating pump is now obstructed, it is possible to use the measured instantaneous value of the initial voltage U BP Off measured at the operating pump in order to calculate the instantaneous value of the admission pressure p v .
  • the two two-way valves 9 , 10 are driven by the control unit 7 as a function of this calculated admission pressure p v . There is thus no need for a complicated measurement of the admission pressure p v by means of a pressure transducer.
  • FIG. 3 shows a method block diagram, in the case of which the operating pump is additionally calibrated in relation to the reference pump.
  • the characteristic curve p v (U RP Off ) is determined between the initial voltage U RP Off and the admission pressure p v for the reference pump in a method step 21 , in particular on a laboratory set-up of the brake system.
  • a histogram H(U RP Off ) for the initial voltage U RP Off is determined for the reference pump, likewise during the test phase I.
  • the characteristic curve p v (U RP Off ) and the histogram H(U RP Off ) are stored in the data memory of the control unit 7 .
  • a special operating pump is calibrated during a calibration phase II. following the test phase I.
  • the operating pump is already installed in this case in a vehicle, particularly in the context of an associated brake system.
  • One histogram H(U BP Off ) each is determined for the initial voltage U BP Off in the calibration phase II.
  • the stipulations for the calibration correspond if possible substantially to those stipulations under which the histogram H(U RP Off ) was determined for the reference pump.
  • the mean values H U RP Off , H U BP Off of the parameters U RP Off and U BP Off are calculated as statistical characteristic variables from the two histograms H U RP Off , H U BP Off determined for the initial voltage U Off .
  • a ratio VZ is calculated from these mean values by forming a quotient
  • VZ ⁇ U BP Off ⁇ ⁇ U RP Off ⁇ .
  • a characteristic curve p v (U BP Off ) of the operating pump is adapted to the characteristic curve p v (U RP Off ) measured for the reference pump in the test phase I. as a function of this ratio VZ.
  • the data acquisition for the histograms H U RP Off and H U BP Off is always performed in the load-free state of the motor vehicle brake system 1 , that is to say with brake pedal 3 unactivated.
  • the calibration phase II. is periodically repeated if required. Moreover, as the calibration is being carried out either automatically by the control unit 7 or manually by a service technician, a check is made as to whether the ratio VZ lies within or outside a prescribed tolerance range. If it is established during this checking that the ratio VZ lies outside the tolerance range, the operating pump is identified as defective. In this case, the control unit 7 outputs a warning signal in the case of automatic checking.
  • the method steps corresponding to the calibration phase II. and the operating phase III. are carried out by the control unit 7 designed as a microcontroller.
  • the calibration phase II. can also be carried out by an external control unit, for example by a workshop measurement computer.
  • the resulting (new) characteristic curve p v (U BP Off ) for the operating pump is transmitted to the control unit 7 and stored in the data memory thereof.
  • the transmission of the characteristic curve p v (U BP Off ) is performed, for example, via a data cable via which the control unit is connected to the external control unit.
  • FIG. 4 shows the histogram H(U RP Off ) for the initial voltage U RP Off of the reference pump.
  • a prescribed operating clock is applied to the motor 15 of the reference pump over a prescribed test period in order to determine the histogram H(U RP Off ).
  • Each measured value U RP Off (t i ) is normalized to the last voltage value U RP OnL (t i ) of the preceding pulse 19 , in formal notation:
  • the voltage values U RP Off (t i ) are assigned, in accordance with their value, voltage intervals that cover the entire spectrum of the measured voltage values U RP Off (t i ).
  • the number of voltage values U RP Off (t i ) that lie in each of the voltage intervals is counted for the purpose of determining the histogram H(U RP Off ).
  • These numerical values yield the histogram H(U RP Off ) in accordance with FIG. 4 when plotted against the initial voltage U RP Off .
  • a mathematical distribution function G which has the form of a Gaussian distribution function is adapted to the histogram H(U RP Off ).
  • the adapted distribution function G is used to determine the mean value U RP Off , which in the case of the Gaussian distribution function corresponds to the maximum thereof.
  • This mean value is stored in the data memory of the control unit 7 .
  • FIG. 5 shows the histogram H(U BP Off ) produced in a corresponding way for the operating pump, together with the Gaussian distribution function G adapted thereto.
  • the control unit 7 determines the mean value U BP Off from the distribution function G.
  • the characteristic curve p v (U BP Off ) for the operating pump stems from the characteristic curve p v (U RP Off ) for the reference pump by a simple multiplication by the ratio VZ.
  • the determined characteristic curve p v (U BP Off ) is now, as already described, stored in the data memory of the control unit 7 .

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Regulating Braking Force (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US12/739,456 2007-10-24 2008-10-22 Method and device for the calibration or diagnosis of a motor vehicle brake system having a cyclically operated pump Expired - Fee Related US8301331B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007050662.9 2007-10-24
DE102007050662A DE102007050662A1 (de) 2007-10-24 2007-10-24 Verfahren und Vorrichtung zur Kalibrierung oder Diagnose einer Kraftfahrzeugbremsanlage mit einer getaktet betriebenen Pumpe
DE102007050662 2007-10-24
PCT/EP2008/064284 WO2009053389A1 (de) 2007-10-24 2008-10-22 Verfahren und vorrichtung zur kalibrierung oder diagnose einer kraftfahrzeugbremsanlage mit einer getaktet betriebenen pumpe

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US20110184606A1 US20110184606A1 (en) 2011-07-28
US8301331B2 true US8301331B2 (en) 2012-10-30

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US (1) US8301331B2 (de)
EP (1) EP2205469B1 (de)
AT (1) ATE507123T1 (de)
DE (2) DE102007050662A1 (de)
WO (1) WO2009053389A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
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US20120112524A1 (en) * 2010-11-10 2012-05-10 Hitachi Automotive Systems, Ltd. Brake control apparatus
US20130226424A1 (en) * 2010-07-30 2013-08-29 Lucas Automotive Gmbh Method of operating an electrically controllable brake system and brake system which is operated according to the method
US20140142826A1 (en) * 2012-11-16 2014-05-22 Nissin Kogyo Co., Ltd. Vehicle brake hydraulic pressure control apparatus

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007050662A1 (de) * 2007-10-24 2009-04-30 Continental Teves Ag & Co. Ohg Verfahren und Vorrichtung zur Kalibrierung oder Diagnose einer Kraftfahrzeugbremsanlage mit einer getaktet betriebenen Pumpe
DE102010028083A1 (de) 2009-04-23 2010-11-11 Continental Teves Ag & Co. Ohg Verfahren zur Kalibrierung eines Pumpenmotors in einer Druckregelanlage
DE102010039818A1 (de) * 2010-08-26 2012-03-01 Continental Teves Ag & Co. Ohg Verfahren zur drucksensorlosen Druckmessung in einem Druckregelaggregat einer Kraftfahrzeugbremsanlage
DE102018203181B4 (de) 2018-03-02 2025-03-06 Volkswagen Aktiengesellschaft Verfahren zur Überprüfung des korrekten Verbaus einer elektronischen Parkbremse eines Kraftfahrzeugs und Prüfanordnung
CN111308932B (zh) * 2020-02-25 2021-08-31 北京百度网讯科技有限公司 刹车系统的标定方法、装置、设备及存储介质
CN113565832B (zh) * 2021-07-19 2024-05-10 奇瑞新能源汽车股份有限公司 自动驾驶车辆的电子助力器液压标定方法、装置及车辆

Citations (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4302812A (en) * 1980-03-31 1981-11-24 Bell Telephone Laboratories, Incorporated Analog signal level monitor
US4745562A (en) * 1985-08-16 1988-05-17 Schlumberger, Limited Signal processing disparity resolution
US4787479A (en) * 1986-09-05 1988-11-29 Lincoln Gmbh Control system for a central lubrication system for vehicle
US5221125A (en) * 1990-06-07 1993-06-22 Toyota Jidosha Kabushiki Kaisha Device for detecting and eliminating accumulator fluid leakage through control valve
DE19651154A1 (de) 1995-12-16 1997-06-19 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Bremsanlage
US5823640A (en) * 1994-08-22 1998-10-20 Robert Bosch Gmbh Method and device for driving an electromagnetic valve
US5971502A (en) * 1998-06-04 1999-10-26 Robert Bosch Technology Corp Secondary braking control
DE19961293A1 (de) 1998-12-28 2000-06-29 Bosch Gmbh Robert Verfahren und Vorrichtung zur Druckermittlung in Bremssystemen
US6092992A (en) * 1996-10-24 2000-07-25 Imblum; Gregory G. System and method for pump control and fault detection
US6102492A (en) * 1997-02-14 2000-08-15 Robert Bosch Gmbh Method and device for controlling braking force distribution in a motor vehicle
US6123395A (en) * 1995-08-04 2000-09-26 Robert Bosch Gmbh Process and device for determining a pressure value
US6188947B1 (en) * 1998-11-09 2001-02-13 Kelsey-Hayes Company Closed loop speed control of ABS pump motor utilizing variable duty cycle and frequency
DE10049506A1 (de) 1999-10-12 2001-04-19 Csi Technology Inc Integrierte Elektromotorüberwachung
US6315369B1 (en) * 1998-12-03 2001-11-13 Toyota Jidosha Kabushiki Kaisha Hydraulic braking system wherein pump motor control PWM frequency is lowered below upper audibility limit under predetermined braking conditions
US6341947B1 (en) * 1999-03-26 2002-01-29 Toyota Jidosha Kabushiki Kaisha Pump device wherein detection of failure of one of pumps causes a change in the manner of control of the pump or pumps to compensate for the failure
US6499813B1 (en) * 1999-04-20 2002-12-31 Robert Bosch Gmbh Method and device for controlling a pump of a brake system
US6604909B2 (en) * 2001-03-27 2003-08-12 Aquatec Water Systems, Inc. Diaphragm pump motor driven by a pulse width modulator circuit and activated by a pressure switch
US6668634B1 (en) * 1999-09-29 2003-12-30 Robert Bosch Gmbh Method and device for estimating an admission pressure in a motor vehicle brake system
US6719377B1 (en) * 1998-04-23 2004-04-13 Robert Bosch Gmbh Method and device for controlling a pump of a brake system
US6741056B1 (en) * 2002-05-15 2004-05-25 Skc, Inc. Air sampler with compensating pump motor speed
US20040105759A1 (en) * 2000-05-02 2004-06-03 Anker Gram High pressure pump system for supplying a cryogenic fluid from a storage tank
WO2005007475A1 (de) 2003-07-11 2005-01-27 Continental Teves Ag & Co.Ohg Elektronisches regelverfahren für eine schlupfgeregelte kraftfahrzeugbremsanlage
US20050069418A1 (en) * 2003-09-25 2005-03-31 Koichi Kokubo Pump drive motor control apparatus
US20050156465A1 (en) * 2002-02-07 2005-07-21 Continental Teves Ag & Co. Ohg Method for determining or calibrating the brake control characteristic of a vacuum brake booster
US7140699B2 (en) * 2002-02-14 2006-11-28 Continental Teves Ag & Co. Ohg Method for regulating a predetermined modifiable brake pressure
DE102005041556A1 (de) 2005-09-01 2007-03-08 Continental Teves Ag & Co. Ohg Verfahren zur Bestimmung eines Vordrucks in einer Kraftfahrzeug-Bremsanlage
US20070210648A1 (en) * 2006-03-13 2007-09-13 Advics Co., Ltd. Brake control device for vehicle
US7346475B2 (en) * 2003-06-18 2008-03-18 Eaton Corporation System and method for proactive motor wellness diagnosis based on potential mechanical faults
US20080191549A1 (en) * 2004-12-06 2008-08-14 Lucas Automotive Gmbh Pressure Generator for a Vehicle Brake System and Method for Mounting Said Pressure Generator
US20100037604A1 (en) * 2006-07-21 2010-02-18 William Hugh Salvin Rampen Fluid power distribution and control system
US7878006B2 (en) * 2004-04-27 2011-02-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US20110184606A1 (en) * 2007-10-24 2011-07-28 Continental Teves Ag & Co. Ohg Method and device for the calibration or diagnosis of a motor vehicle brake system having a cyclically operated pump
US8133034B2 (en) * 2004-04-09 2012-03-13 Regal Beloit Epc Inc. Controller for a motor and a method of controlling the motor
US8160827B2 (en) * 2007-11-02 2012-04-17 Emerson Climate Technologies, Inc. Compressor sensor module
US8177520B2 (en) * 2004-04-09 2012-05-15 Regal Beloit Epc Inc. Controller for a motor and a method of controlling the motor
US8177519B2 (en) * 2006-10-13 2012-05-15 Regal Beloit Epc Inc. Controller for a motor and a method of controlling the motor

Patent Citations (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4302812A (en) * 1980-03-31 1981-11-24 Bell Telephone Laboratories, Incorporated Analog signal level monitor
US4745562A (en) * 1985-08-16 1988-05-17 Schlumberger, Limited Signal processing disparity resolution
US4787479A (en) * 1986-09-05 1988-11-29 Lincoln Gmbh Control system for a central lubrication system for vehicle
US5221125A (en) * 1990-06-07 1993-06-22 Toyota Jidosha Kabushiki Kaisha Device for detecting and eliminating accumulator fluid leakage through control valve
US5823640A (en) * 1994-08-22 1998-10-20 Robert Bosch Gmbh Method and device for driving an electromagnetic valve
US6123395A (en) * 1995-08-04 2000-09-26 Robert Bosch Gmbh Process and device for determining a pressure value
DE19651154A1 (de) 1995-12-16 1997-06-19 Bosch Gmbh Robert Verfahren und Vorrichtung zur Steuerung einer Bremsanlage
US6092992A (en) * 1996-10-24 2000-07-25 Imblum; Gregory G. System and method for pump control and fault detection
US6102492A (en) * 1997-02-14 2000-08-15 Robert Bosch Gmbh Method and device for controlling braking force distribution in a motor vehicle
US6719377B1 (en) * 1998-04-23 2004-04-13 Robert Bosch Gmbh Method and device for controlling a pump of a brake system
US5971502A (en) * 1998-06-04 1999-10-26 Robert Bosch Technology Corp Secondary braking control
US6188947B1 (en) * 1998-11-09 2001-02-13 Kelsey-Hayes Company Closed loop speed control of ABS pump motor utilizing variable duty cycle and frequency
US6315369B1 (en) * 1998-12-03 2001-11-13 Toyota Jidosha Kabushiki Kaisha Hydraulic braking system wherein pump motor control PWM frequency is lowered below upper audibility limit under predetermined braking conditions
DE19961293A1 (de) 1998-12-28 2000-06-29 Bosch Gmbh Robert Verfahren und Vorrichtung zur Druckermittlung in Bremssystemen
US6446490B1 (en) * 1998-12-28 2002-09-10 Robert Bosch Gmbh Method and device for determining the pressure in brake systems
US6341947B1 (en) * 1999-03-26 2002-01-29 Toyota Jidosha Kabushiki Kaisha Pump device wherein detection of failure of one of pumps causes a change in the manner of control of the pump or pumps to compensate for the failure
US20030080611A1 (en) * 1999-04-20 2003-05-01 Helmut Wandel Method and device for controlling a pump of a brake system
US6499813B1 (en) * 1999-04-20 2002-12-31 Robert Bosch Gmbh Method and device for controlling a pump of a brake system
US6668634B1 (en) * 1999-09-29 2003-12-30 Robert Bosch Gmbh Method and device for estimating an admission pressure in a motor vehicle brake system
US6529135B1 (en) * 1999-10-12 2003-03-04 Csi Technology, Inc. Integrated electric motor monitor
DE10049506A1 (de) 1999-10-12 2001-04-19 Csi Technology Inc Integrierte Elektromotorüberwachung
US20040105759A1 (en) * 2000-05-02 2004-06-03 Anker Gram High pressure pump system for supplying a cryogenic fluid from a storage tank
US6604909B2 (en) * 2001-03-27 2003-08-12 Aquatec Water Systems, Inc. Diaphragm pump motor driven by a pulse width modulator circuit and activated by a pressure switch
US20050156465A1 (en) * 2002-02-07 2005-07-21 Continental Teves Ag & Co. Ohg Method for determining or calibrating the brake control characteristic of a vacuum brake booster
US7140699B2 (en) * 2002-02-14 2006-11-28 Continental Teves Ag & Co. Ohg Method for regulating a predetermined modifiable brake pressure
US6741056B1 (en) * 2002-05-15 2004-05-25 Skc, Inc. Air sampler with compensating pump motor speed
US7346475B2 (en) * 2003-06-18 2008-03-18 Eaton Corporation System and method for proactive motor wellness diagnosis based on potential mechanical faults
US20060202552A1 (en) 2003-07-11 2006-09-14 Continental Teves Ag & Co.Ohg Electronic control method for a slip-controlled motor vehicle brake system
WO2005007475A1 (de) 2003-07-11 2005-01-27 Continental Teves Ag & Co.Ohg Elektronisches regelverfahren für eine schlupfgeregelte kraftfahrzeugbremsanlage
US20050069418A1 (en) * 2003-09-25 2005-03-31 Koichi Kokubo Pump drive motor control apparatus
US8177520B2 (en) * 2004-04-09 2012-05-15 Regal Beloit Epc Inc. Controller for a motor and a method of controlling the motor
US8133034B2 (en) * 2004-04-09 2012-03-13 Regal Beloit Epc Inc. Controller for a motor and a method of controlling the motor
US7878006B2 (en) * 2004-04-27 2011-02-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US7905098B2 (en) * 2004-04-27 2011-03-15 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US20080191549A1 (en) * 2004-12-06 2008-08-14 Lucas Automotive Gmbh Pressure Generator for a Vehicle Brake System and Method for Mounting Said Pressure Generator
DE102005041556A1 (de) 2005-09-01 2007-03-08 Continental Teves Ag & Co. Ohg Verfahren zur Bestimmung eines Vordrucks in einer Kraftfahrzeug-Bremsanlage
US20080231108A1 (en) 2005-09-01 2008-09-25 Continental Teves Ag & Co. O Hg Method of Determining an Initial Pressure in a Motor Vehicle Brake System
US20070210648A1 (en) * 2006-03-13 2007-09-13 Advics Co., Ltd. Brake control device for vehicle
US20100037604A1 (en) * 2006-07-21 2010-02-18 William Hugh Salvin Rampen Fluid power distribution and control system
US8177519B2 (en) * 2006-10-13 2012-05-15 Regal Beloit Epc Inc. Controller for a motor and a method of controlling the motor
US20110184606A1 (en) * 2007-10-24 2011-07-28 Continental Teves Ag & Co. Ohg Method and device for the calibration or diagnosis of a motor vehicle brake system having a cyclically operated pump
US8160827B2 (en) * 2007-11-02 2012-04-17 Emerson Climate Technologies, Inc. Compressor sensor module

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130226424A1 (en) * 2010-07-30 2013-08-29 Lucas Automotive Gmbh Method of operating an electrically controllable brake system and brake system which is operated according to the method
US9085289B2 (en) * 2010-07-30 2015-07-21 Lucas Automotive Gmbh Method of operating an electrically controllable brake system and brake system which is operated according to the method
US20120112524A1 (en) * 2010-11-10 2012-05-10 Hitachi Automotive Systems, Ltd. Brake control apparatus
US20140142826A1 (en) * 2012-11-16 2014-05-22 Nissin Kogyo Co., Ltd. Vehicle brake hydraulic pressure control apparatus
CN103818367A (zh) * 2012-11-16 2014-05-28 日信工业株式会社 车辆用制动液压控制装置
US9346448B2 (en) * 2012-11-16 2016-05-24 Nissin Kogyo Co., Ltd Vehicle brake hydraulic pressure control apparatus with pump motor malfunction detection
CN103818367B (zh) * 2012-11-16 2017-02-01 日本奥托立夫日信制动器系统株式会社 车辆用制动液压控制装置

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DE102007050662A1 (de) 2009-04-30
US20110184606A1 (en) 2011-07-28

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